HINGE ACTUATOR AND METHOD FOR ADJUSTING TWO PARTS OF A HINGE ACTUATOR RELATIVE TO EACH OTHER

Description

[0001] The invention relates to a hinge actuator according to the preamble of claim 1.

[0002] Such a hinge actuator is known, for instance from WO 03/011642, as used in a mirror adjustment mechanism for a wing mirror unit of a motor vehicle. The first part of the actuator is fixedly mounted on the motor vehicle. The second part supports a mirror housing and can pivot relative to the first part to the predetermined position, for instance a fold-in position to reduce the width of the vehicle, for instance after parking, or a fold-out position for use of the wing mirror unit under normal operating conditions. The predetermined position is defined by the stops cooperating in the pivoting direction, so that further pivoting is prevented.

[0003] The two parts of the hinge actuator can be pivoted both electrically and non-electrically, for instance manually. By the use of the coupling between the two parts, the electric drive can be uncoupled so that a pivoting movement of the wing mirror unit not caused by the drive, for instance upon manual pivoting, does not force any movements of the drive, and damage to the electric drive, such as fractures in a drive train or defects in an electric motor, can be prevented.

[0004] It is desired to define the predetermined position of the mirror housing so well that unintended pivoting back is prevented. As a consequence, the influence of external forces exerted on the mirror housing, such as air flowing along the wing mirror unit, for instance gusts of wind or driving wind, is reduced. By the provision of an additional pair of stops which cooperate in the predetermined position in an opposite pivoting direction, this problem could be mitigated. In order to enable electrical pivoting back from the predetermined position, the reaction force caused by the additional pair of stops should not exceed a predetermined level when pivoting electrically, since the drive must be able to overcome the reaction force.

[0005] In addition, however, it is desirable that the mirror housing, upon manual adjustment to the predetermined position, be secured in such a way that a clearly sensible coupling or 'click' can be felt and that the force that is needed to adjust the mirror housing further in the pivoting direction is of the same order of magnitude as the required force for pivoting the mirror housing in a direction opposite to the pivoting direction. To realize this, the reaction forces caused by the stops should be of the same order of magnitude in both directions. However, the electric drive then cannot adjust the mirror housing from the predetermined position, unless unacceptably powerful and costly electric motors are used, or the reaction forces caused by the stops are so slight that upon manual adjustment no resistance of significance is sensed.

[0006] The object of the invention is to provide a hinge actuator of the type mentioned in the opening paragraph hereof, in which, while preserving the advantages, the disadvantages mentioned are avoided. In particular, the object of the invention is to obtain a hinge actuator where, in the case of manual operation, a clearly sensible coupling can be sensed upon the predetermined position being reached, and where, with the aid of the electric drive, still pivoting movement from the predetermined position in the opposite pivoting direction is possible. To that end, a hinge actuator according to claim 1 is provided.

[0007] As the stops cooperating in the opposite pivoting direction are only active in the second position of the coupling, in which the first part and the second part are not connected via the drive, what is achieved is that the stops cooperating in the opposite pivoting direction, upon manual operation can cause a reaction force which is of the same order of magnitude as the reaction force caused by the stops cooperating in the pivoting direction. As a result, upon manual operation, a clear coupling is sensible. Moreover, the electric drive can still pivot the first part relative to the second part in the opposite pivoting direction, also from the predetermined position, since the stops cooperating in the opposite pivoting direction are not active in the first position of the coupling, in which the electric drive can pivot the first and second parts relative to each other.

[0008] Also with manual operation, in case of external forces on the hinge actuator, such as wind, undesired pivoting movement is prevented, since a powerful coupling in the predetermined position has been obtained.

[0009] Preferably, the first part of the hinge actuator comprises a base plate, provided with a base shaft, while the second part comprises a supporting frame extending around the base shaft for supporting a mirror housing, so that the hinge actuator can be used in a mirror adjustment mechanism for a wing mirror unit of a motor vehicle.

[0010] By designing the coupling with a coupling ring which is disengageably rotation-coupled and axially movable relative to the base shaft, the first and the second position can be defined in a relatively simple manner. The coupling ring can, for instance, be disengageably rotation-coupled with the base shaft by means of a cam construction which permits a pivoting movement upon the occurrence of an external couple greater than a pre-set level. Due to the fact that the rotation coupling of the coupling ring then disengages, the coupling ring also moves axially from a first axial position which defines the first position to a second axial position which defines the second axial position. When upon pivoting of the first part relative to the second part of the hinge actuator the coupling re-engages, the coupling ring moves back again to the first axial position. Of course, for reliably defining the axial positions of the coupling ring, also other disengageable constructions can be used, such as, for instance, roller elements in guide tracks.

[0011] By designing the stops cooperating in the opposite pivoting direction in such a way that the occurring reaction forces are in the same order of magnitude as the reaction forces occurring upon cooperation of the stops in the pivoting direction, what is achieved is that upon manual adjustment of the hinge actuator a clear coupling can be sensed upon the predetermined position being reached. The force that is needed for pivoting further or back is then in the same order of magnitude.

[0012] Advantageously, the hinge actuator can be provided with a switch-off mechanism for switching off the drive, whereby the force needed to overcome the stops cooperating in the opposite pivoting direction is in the same order of magnitude as the force at which the drive is switched off by the switch-off mechanism. What is thereby achieved is that the electric drive upon the predetermined position being reached, switches off automatically, so that the drive is not unduly loaded and premature wear is prevented. Since the required force for switching off is tuned to the same order of magnitude as the force that is required to overcome the stops cooperating in the opposite pivoting direction with manual operation, the user will upon manual adjustment of the hinge actuator experience a clear coupling upon the predetermined position being reached. As desired, the required force for removing the coupling is then of the same order of magnitude in both directions.

[0013] Preferably, the cooperating stops are formed by at least one cam which is arranged on the supporting frame for traversing a path during the pivoting movement of the supporting frame, and at least one first stop positioned fixedly with respect to the base shaft, and wherein the stops cooperating in an opposite pivoting direction are formed by the cam which is arranged on the supporting frame and at least one second stop arranged so as to be axially movable with respect to the base shaft. In this way, the cam on the supporting frame cooperates elegantly with both the first stop which prevents pivoting in the pivoting direction, and the second, movable stop which prevents pivoting movement in the opposite pivoting direction when the coupling is in the second position.

[0014] Further advantageous embodiments of the invention are represented in the subclaims.

[0015] The invention will be further elucidated on the basis of exemplary embodiments which are represented in the drawing. In the drawing:

Fig. 1 is a first perspective view of a hinge actuator according to the invention in disassembled condition;

Fig. 2 is a second perspective view of the hinge actuator of Fig. 1;

Fig. 3 is a perspective view of a base ring and an auxiliary ring of the hinge actuator of Fig. 1;

Fig. 4 is a perspective view of a gear wheel and a base flange of the hinge actuator of Fig. 1;

Fig. 5 is a schematic perspective view of an alternative embodiment of the hinge actuator in disassembled condition;

Fig. 6 is a schematic perspective view of the hinge actuator of Fig. 5 in assembled condition with the coupling in the first position; and

Fig. 7 is a schematic perspective view of the hinge actuator of Fig. 6 in assembled condition with the coupling in the second position.

[0016] The figures are only schematic representations of preferred embodiments of the invention. In the figures, the same or corresponding parts are indicated with the same reference numerals.

[0017] Figures 1 and 2 show a preferred embodiment of a hinge actuator 1. The hinge actuator 1 has a first part, designed as a base part 2, and a second part, designed as a supporting frame 3, which parts can pivot relative to each other. The base part 2 can be fixedly connected to a motor vehicle, and has a base flange 4 on which a fixed base shaft 5 is arranged. The base shaft 5 extends along a geometric pivoting axis A of substantially upstanding orientation. The supporting frame 3 is built up from modules fixedly attached to each other and extends around the base shaft 5 and can support a mirror housing which accommodates a mirror glass, so that the whole can serve as a wing mirror unit of a motor vehicle. During pivoting of the hinge actuator 1, the supporting frame 3 hinges about the base shaft 5.

[0018] Arranged on the base flange 4 is a base ring 7 which likewise extends around the base shaft 5. The side of the base ring 7 remote from the base flange 4 is at least partly formed as a first cam track 8 to be traversed by a cam 9 which is fixedly attached to the supporting frame 3 via a cam ring 10. The cam track 8 comprises a substantially planar portion which is bounded at the ends by two inclined butting faces 8a, 8b which form stops cooperating with the cam 9 in a pivoting direction for defining a predetermined position of the actuator parts relative to each other, such as a fold-in position of the wing mirror unit which is suitable for performing parking maneuvers and a fold-out position for normal use of the motor vehicle in traffic.

[0019] The supporting frame 3 accommodates an electric motor, not shown, and a drive train coupled thereto, which constitute the drive of the hinge actuator. The drive train is further adapted to be coupled with the coupling ring designed as gear wheel 12, which constitutes a coupling between the drive and a driven part of the actuator 1. The gear wheel 12 encloses the base shaft 5 and is arranged so as to be axially movable relative thereto and further, in a first position situated near the base flange 4, restrained from rotation relative to the base shaft 5. With the aid of a biased spring element, not shown, the gear wheel 12 is driven in the direction of the base flange 4. The gear wheel 12 is in engagement with an output part of the drive train, so that the hinge actuator 1 can be adjusted with the drive.

[0020] During manual operation of the hinge actuator 1, the lock against rotation of the gear wheel 12 with respect to the base shaft 5 is disengaged by the externally applied force, for instance by uncoupling a cam construction 11 arranged between the base flange 4 and the gear wheel 12, as shown in more detail in Fig. 4. The cam construction 11 comprises at least one cam 11a and a cam track 11b which are respectively provided on a flange ring 4a which is restrained from rotation relative to the base flange 4, and on the gear wheel 12, or vice versa. As a result, the gear wheel 12 moves axially, against the spring action of the spring element, from the first position to a second position, situated farther from the base flange 4, in which the gear wheel 12 is freely rotatable relative to the base shaft 5. In the second position of the gear wheel 12, the supporting frame 3 can be manually pivoted relative to the base shaft 5. This enables a manual pivoting of the wing mirror unit relative to the motor vehicle without forcing movements of the drive. Upon subsequent switching on of the electric drive, the gear wheel 12 couples with the base flange 4, so that electric adjustment is possible again.

[0021] The hinge actuator 1 furthermore comprises an auxiliary ring 13 which encloses the base shaft 5 and, under spring action of the spring element, abuts against the gear wheel 12. The auxiliary ring 13 is shown in more detail in Fig. 3 and, with the aid of cams 14 and recesses 15, is axially movable, though restrained from rotation relative to the base ring 7, so that the auxiliary ring 13 can follow the axial movements of the gear wheel 12. The side of the auxiliary ring 13 remote from the base flange 4 is at least partly formed as a second cam track 16 to be traversed by the cam 9 arranged on the supporting frame 3. The second cam track has inclined butting faces 16a,16b, so that pivoting of the supporting frame 3 from the predetermined position in the opposite pivoting direction is prevented.

[0022] When the gear wheel is in the first position, the hinge actuator 1 can be adjusted with the aid of the electric drive. The cam 9 of the supporting frame 3 then traverses a path which is defined by the first cam track 8, since the second cam track cannot come into contact with the cam 9 in the first position of the gear wheel 12. Upon reaching a butting face 8a, 8b of the first cam track 8, the cam 9 forms therewith a pair of stops cooperating in the pivoting direction, causing a reaction force whereby the electric motor 10 switches off in the predetermined position. The hinge actuator can pivot back electrically by activating the electric motor 10 in the opposite pivoting direction.

[0023] As described above; manual adjustment of the actuator is possible by bringing the gear wheel 12 in the second position, as a result of which the electric drive is uncoupled. The gear wheel 12 further pushes the auxiliary ring 13 in the direction directed away from the base flange 4, so that the second cam track 16 can also limit the path of the cam 9. Upon manual pivoting of the hinge actuator 1, the cam 9 will again form, together with a butting face 8a, 8b of the first cam track 8, a pair of stops cooperating in the pivoting direction, thereby preventing further pivoting in the pivoting direction. The occurring reaction forces are a signal to the user that further pivoting is probably undesired, because a position which is desired for the user of the motor vehicle has already been obtained or because further pivoting is not possible in terms of construction technique. Also pivoting back is now prevented by the cam 9 which, together with a butting face 16a, 16b of the second cam track 16, forms a pair of stops cooperating in the opposite pivoting direction. As a result, the person performing the pivoting movement experiences a clearly noticeable coupling in the predetermined position of the supporting frame 3 with respect to the base shaft 5. Owing to the specific shape and dimensions of the butting faces 8a, 8b, 16a, 16b, the required force to overcome the two pairs of cooperating stops is in the same order of magnitude. The cam 9 is oriented so broadly that cooperation with the butting faces of both the first and the second cam track 8, 16 is possible. Instead of one integrated cam 9, however, two cams may be arranged which, if desired, can include an angle relative to each other. Also in the case of other pivoting movement of the hinge actuator, not caused by the drive, for instance upon contact with a foreign object, such as a pillar, the above-outlined interplay of forces occurs.

[0024] The hinge actuator 1 furthermore comprises a current limiting circuit which serves as a switch-off mechanism. When, upon the supporting frame 3 and the base shaft 5 reaching the predetermined position, the electric current in the electric motor increases in order to generate a sufficient couple, the current limiting circuit switches off the electric motor at a predetermined current intensity, so that damage to the electric motor is prevented. The butting faces 16a, 16b of the second cam track 16 are so designed that overcoming the reaction forces caused with the cam 9 in the predetermined position of the hinge actuator would generate such a large current in the electric motor that the current limiting circuit would enter into operation and switch off the electric motor.

[0025] Optionally, the hinge actuator may furthermore be provided with a resilient ring for driving the auxiliary ring in the direction of the base flange in order to prevent stops being able to cooperate in the opposite pivoting direction when the first and second part of the actuator are connected with each other via the drive.

[0026] Figures 5, 6 and 7 show an alternative preferred embodiment of the hinge actuator 101. The hinge actuator 101 has a first part, designed as a base part 102, and a second part, designed as a supporting frame 103, which parts can pivot relative to each other. The base part 102 can be fixedly connected to a motor vehicle, and has a base flange 104 on which a fixed base shaft 105 is arranged. The supporting frame 103 is built up from modules fixedly mounted on each other, extends around the base shaft 105 and can support a mirror housing in which a mirror glass is included, so that the whole can serve as a wing mirror unit of a motor vehicle. During pivoting of the hinge actuator 101, the supporting frame 103 hinges about the base shaft 105.

[0027] Formed on the base flange 104 is a cam track 108 which can be traversed by a cam 109 which is fixedly mounted on the supporting frame 103. In the figure, for the sake of clarity, this part of the base frame is represented as a separate cam ring 110. It will be clear that the cam ring 110 may be integrated with the bottom of the supporting frame 103. The cam track 108 comprises a substantially planar portion which is bounded at the ends by an inclined butting face 108a which cooperates in the pivoting direction indicated by the arrow P with a corresponding stop surface 109a of the cam 109. The stop surfaces 108a, 109a form cooperating stops for defining in a first pivoting direction a predetermined position of the actuator parts 102, 103 with respect to each other. In the figure, this is represented as a fold-out position of the wing mirror unit during normal use of the motor vehicle in traffic, which is defined in the fold-out direction.

[0028] Included in the supporting frame 103 is an electric motor 120 with a drive train 121 coupled to it, which constitute the drive of the hinge actuator. The output part of the drive is formed as a gear wheel 112 which is arranged as a coupling ring around the base shaft 105. The gear wheel 112 and the base shaft 105 together constitute a coupling 111 so that, in the first position of the coupling, the base part 102 and the supporting frame 103 are connected via the drive and can be pivoted relative to each other with the drive, and in a second position, the base part 102 and the supporting frame 103 are not connected via the drive and can be pivoted relative to each other manually.

[0029] The gear wheel 112 encloses the base shaft 105 and is so arranged as to be axially movable relative thereto. In a first position, situated axially closer to the base flange 104, the gear wheel 112 is further restrained from rotation, that is, rotation-coupled with respect to the base shaft 105.

[0030] During application of an external force on the hinge actuator 101, as in the case of manual operation, the lock against rotation of the gear wheel 112 relative to the base shaft 105 can be disengaged by uncoupling the coupling 111 between the gear wheel 112 and the base shaft 105.

[0031] To that end, the coupling 111 comprises, on the one hand, three two-topped profiles 122 arranged on the circumference of the base shaft 105 and, on the other hand, cams 123 reaching downwards with respect to the gear wheel 112 for cooperation with the two-topped profiles. In the first position of the coupling, the gear wheel 112, in a first axial position, is supported axially on the base shaft 105 and locked against rotation in that the cams 123 are each lodged in valleys 124 between tops 125 of the two-topped cam track profiles 122. In the first position of the coupling 111, the gear wheel 112 is axially movable from a first axial position, in an axial direction directed away from the base flange 104, to a second axial position.

[0032] When under the influence of an external force the supporting frame 103 is rotated about the base shaft 105, the gear wheel 112 is carried along by the drive train 121, and the cams 123 are guided axially upwards via the flanks of the tops 125 contiguous to the valley 124. After passing the tops 125, the cams will be guided downwards under the action of a coil spring 106 arranged around the base shaft 105, along the inclined flanks of the two-topped profile 122 remote from the valleys, down onto a top surface of an auxiliary coupling ring 126 arranged around the base shaft 105 between the gear wheel 112 and the supporting frame 103, so that the gear wheel 112 reaches a second axial position in which it is freely rotatable relative to the base shaft 105. The function of the auxiliary coupling ring 126 will be further elucidated hereinafter.

[0033] The coupling 111 enables a manual pivoting of the wing mirror unit relative to the motor vehicle without forcing movements of the drive.

[0034] By the use of the coupling 111, the supporting frame 103 can therefore be pivoted around the base part through both electric drive and manual operation. The fold-out position is then defined in a first pivoting direction, i.e. towards the fold-out position, by cooperation of the stop surfaces 8a, 9a.

[0035] During pivoting in the first direction towards the fold-out position, the electric operation can be switched off with the aid of a current limiting circuit 130. When, upon reaching the predetermined position of the supporting frame 103 through cooperation of the stops 108a, 108b, the electric current in the electric motor increases, the current limiting circuit 130 switches off the electric motor at a predetermined current intensity, thereby preventing damage to the electric motor or drive train.

[0036] Under the influence of an external force, the cooperating stops 108a, 109a can be overcome against the action of the spring 106, so that the base frame 103 can be pivoted further in the direction of the arrow P to a fold-over position. The supporting frame 103 can then be pivoted back both with the aid of the electric drive and manually.

[0037] When the first and the second part are connected via the drive, the fold-out position is defined in the opposite pivoting direction in that the drive prevents pivoting.

[0038] For defining the fold-in position in the case of manual operation in the opposite pivoting direction, i.e. in the inward pivoting direction, the hinge actuator 101 is equipped with an auxiliary coupling ring 126 which is arranged around the base shaft 105. The auxiliary coupling ring 126 is arranged between the gear wheel 112 and the supporting frame 103. The auxiliary coupling ring 126 and the mirror supporting frame 103 are provided with auxiliary stops 127, 128 cooperating only in the second position of the coupling 111 in the opposite pivoting direction. These auxiliary stops therefore constitute the stops for defining the predetermined position in the opposite pivoting direction. The auxiliary coupling ring 126 is arranged around the base shaft 105 so as to be axially movable and rotation-coupled. The auxiliary stops 128 are formed by stop surfaces 128a on two cam tracks 128' which are provided on the undersurface of the auxiliary coupling ring 126. The auxiliary stop surfaces 127 are formed by stop surfaces 127a which are provided on two upwardly reaching cams 127' on the supporting frame 103. As will be elucidated hereinafter, the cam tracks 128' and the cams 127' cooperate to define the fold-out position in the fold-in direction when as a result of an externally applied force the coupling is in the second position, and the cams 123 of the gear wheel 112 therefore rest on the top surface of the auxiliary coupling ring 126. It will be clear that the cams 127' and the cam tracks 128 can also be interchanged.

[0039] The hinge actuator 101 further comprises an intermediate ring 129, arranged around the base shaft, which is under axial action of the spring 106. In a first position of the coupling 111, the intermediate ring 129 is supported directly on the supporting frame 103. In the second position of the coupling 111, the upper surface of the gear wheel 112 is in the second position, which is situated axially farther from the base flange 104 than the first position. The intermediate ring 129 is then supported on the upper surface of the gear wheel 112. As a result, when the gear wheel 112, as described above, has been brought into the second position upon manual pivoting of the supporting frame 103, the auxiliary coupling ring 126 will become subject to spring action. What is thus achieved is that in the first position of the coupling, in which the gear wheel 112 is supported on the base shaft 105 while the auxiliary coupling ring is freely movable with limited travel, the cams 127' on the auxiliary coupling ring 126 do not cooperate under spring action with the cam tracks 128'. As a result, the stop surfaces 127a, 128a will not cooperate as stops during electrically-driven inward pivoting from the fold-out position. Upon electrically-driven inward pivoting, the auxiliary coupling ring 126 will be moved axially upwards and permit pivoting without resistance of significance.

[0040] What can optionally be achieved by providing a slight friction between the auxiliary coupling ring and the base shaft 105, is that the auxiliary stop surfaces 127', 128' are axially spaced apart during normal (electric) operation and hence do not touch upon being pivoted relative to each other.

[0041] In the second position of the coupling, however, the auxiliary coupling ring 126 is under downward spring action via the gear wheel 112, which is now in the second position. The auxiliary coupling ring 126 transmits the spring force to the supporting frame 103, viz. in that the auxiliary cam 127' is pressed onto the auxiliary cam track 128'. When the supporting frame is pivoted further to the predetermined position, the auxiliary cam 127 will follow the auxiliary cam-track 128 and be guided along auxiliary stop surface 128a to a higher supporting surface 128" of the cam track 128'.

[0042] As a result, the auxiliary coupling ring 126, together with the gear wheel 112, will undergo a downward movement, i.e. towards the base flange 104. In the process, however, the two preferably remain under spring action. The downward movement is limited in that the stop surfaces 127' and 128a' cooperate in the opposite pivoting direction, and also in that top surfaces 127" of auxiliary cams 127' and supporting surfaces 128" of the cam tracks 128' cooperate, so that eventually the predetermined position is defined. As the fold-out position is approached during folding out, this will be experienced by the pivoting person as a clear 'click'.

[0043] After a manual pivoting to the fold-out position as described above, then, upon manual operation in the opposite pivoting direction, first the stops 27', 28a' will have to be overcome against the action of the spring 106, so that a clear 'click' can be felt again. The auxiliary coupling ring 126 is then pressed upwards, together with gear wheel 112, against the spring action. In this way, therefore, it is possible upon manual operation to feel a clear 'click' both upon outward pivoting to the fold-out position and upon pivoting back from the fold-out position, while this 'click' can remain absent in the case of electrical pivoting back.

[0044] The invention is not limited to the exemplary embodiments described here. Many variants are possible.

[0045] Thus, the coupling ring designed as gear wheel can be designed differently, for instance as a ring which constitutes a disengageable coupling between a driven part of the electric drive and a first or second part of the hinge actuator.

[0046] Also, the cam may be fixed on the base ring, with butting faces provided on the supporting frame and the auxiliary ring. The auxiliary ring is then locked against rotation with respect to the supporting frame. Furthermore, the cam tracks and the cam can be of eccentric or other design.

[0047] Furthermore, the switch-off mechanism, instead of being designed as a current limiting circuit, can also be designed with the aid of a different mechanism, for instance with the aid of a friction coupling.

[0048] Such variants will be clear to those skilled in the art and are understood to fall within the scope of the invention as set forth in the following claims.

Claims

1. A hinge actuator (1, 101) comprising a first part (2; 102) which is connected with a second part (3; 103) via an electric drive, wherein the first and the second part (3; 103) are provided with stops (8a, 8b, 9; 108a, 109a) cooperating in a pivoting direction for defining a predetermined position of the actuator parts with respect to each other, wherein further a coupling (12; 111) is provided between the first and the second part, so that in a first position of the coupling (12; 111) the first part (2; 102) and the second part (3; 103) are connected via the drive and can be pivoted relative to each other with the drive, and in a second position the first part (2; 102) and the second part (3; 103) are not connected via the drive and can be pivoted relative to each other manually, characterized in that the first and the second part (3; 103) are furthermore provided with stops (16a, 16b, 9; 127, 128) only cooperating in the second position of the coupling (12; 111) in an opposite pivoting direction, for defining the predetermined position, which stops (16a, 16b, 9; 127, 128) are not active in the first position of the coupling (12; 111), and are only active in the second position of the coupling (12; 111).

2. A hinge actuator according to claim 1, wherein the first part (2; 102) comprises a base plate (4; 104), provided with a base shaft (5; 105), and wherein the second part (3; 103) comprises a supporting frame 3 extending around the base shaft (5; 105), for supporting a mirror housing.

3. A hinge actuator according to claim 2, wherein the coupling (12; 111) comprises a coupling ring which with respect to the base shaft (5; 105) is disengageably rotation-coupled and axially movable between the first and the second position.

4. A hinge actuator according to any one of the preceding claims, wherein the stops (16a, 16b, 9; 127, 128) cooperating in the opposite pivoting direction are so arranged that the occurring reaction forces are in the same order of magnitude as the reaction forces occurring upon cooperation of the stops in the pivoting direction.

5. A hinge actuator according to any one of the preceding claims, wherein the actuator is provided with a switch-off mechanism for switching off the drive, and wherein the force required for overcoming the stops (16a, 16b, 9; 127, 128) cooperating in the opposite pivoting direction is of at least the same order of magnitude as the force at which the drive is switched off by the switch-off mechanism.

6. A hinge actuator according to claim 5, wherein the switch-off mechanism comprises a current limiting circuit, and wherein the electric current in the electric drive needed to overcome the stops (16a, 16b) cooperating in the opposite pivoting direction is of at least the same order of magnitude as the current at which the current limiting circuit switches off the drive.

7. A hinge actuator according to any one of claims 2-6, wherein the cooperating stops are formed by at least one cam (9; 109) which is arranged on the supporting frame for traversing a path during pivoting of the supporting frame and at least one first stop (8a, 8b; 108a), positioned fixedly with respect to the base shaft, and wherein the stops (16a, 16b, 9; 127, 128) cooperating in an opposite pivoting direction are formed by the cam (16a, 16b; 127) which is arranged on the supporting frame and at least one second stop (9; 128) which is arranged so as to be axially movable relative to the base shaft.

8. A hinge actuator according to any one of claims 3-7, wherein the coupling ring is designed as a gear wheel (12; 112) which is in engagement with an output part of the electric drive and which in the first position is locked against rotation relative to the base shaft (5; 105) and in the second position is freely rotatable relative to the base shaft.

9. A hinge actuator according to any one of claims 3-8, wherein between coupling ring and mirror supporting frame, an auxiliary coupling ring (13; 126) is included around the base shaft.

10. A hinge actuator according to claim 9, wherein auxiliary coupling ring (13; 126) and mirror supporting frame are provided with auxiliary stops (16a, 16b; 128) cooperating in the second position of the coupling (12; 111) in the opposite pivoting direction, which constitute the stops for defining the predetermined position in the opposite pivoting direction.

11. A hinge actuator according to any one of the preceding claims, further comprising an intermediate ring (129) arranged around the base shaft (105), which is under axial spring action and which in the first position of the coupling (111) is supported on the mirror supporting frame and which in the second position is supported on the coupling ring (126).

12. A hinge actuator according to any one of claims 3-11, wherein the base shaft (105) at its circumference is provided with a number of two-topped profiles (122), and wherein the coupling ring (126) is provided with cams, each for cooperation with the two-topped profiles.

13. A hinge actuator according to claim 12, wherein the coupling ring, in a first position of the coupling, in a first axial position is supported in axial direction on the base shaft (105) and is locked against rotation via cams which are received in valleys between the two-topped profile.

14. A hinge actuator according to any one of claims 3-13, wherein the coupling ring (126) in the first position of the coupling (111) is axially movable from a first axial position to a second axial position.

15. A hinge actuator according to any one of the preceding claims 9-14, wherein the coupling ring in the second position of the coupling (12; 111) is supported on the auxiliary coupling ring (13; 126).

16. A hinge actuator according to claim 15, wherein the coupling ring, in the second position of the coupling, in a second axial position is under axial spring action in the direction of the first position and is supported on the auxiliary coupling ring (13; 113) via downwardly reaching cams.

17. A hinge actuator according to any one of the preceding claims, wherein the auxiliary coupling ring (13; 113) in the second position is supported on the supporting frame.

18. A hinge actuator according to claim 7, wherein the path in the first position of the coupling ring is formed by a first cam track which is provided on a base ring which is mounted fixedly with respect to the base shaft (5; 105), and wherein the path in the second position of the coupling ring is partly formed by a second cam track which is provided on an auxiliary ring which is locked against rotation and axially movable relative to the base ring.

19. A hinge actuator according to claim 18, wherein the auxiliary ring (13; 126) abuts against the coupling ring.

Ansprüche

1. Gelenkaktuator (1,101) mit einem ersten Teil (2;102), der über einen elektrischen Antrieb mit einem zweiten Teil (3;103) verbunden ist, wobei der erste und der zweite Teil (3;103) Anschläge (8a,8b,9;108a, 109a) aufweisen, die in Schwenkrichtung zusammenwirken, um eine vorbestimmte Position der Aktuatorteile relativ zueinander zu definieren, wobei ferner eine Kupplung (12;111) derart zwischen dem ersten und dem zweiten Teil vorgesehen ist, dass in einer ersten Position der Kupplung (12;111) der erste Teil (2;102) und der zweite Teil (3;103) über den Antrieb miteinander verbunden sind und relativ zueinander über den Antrieb schwenkbar sind, und in einer zweiten Position der erste Teil (2;102) und der zweite Teil (3;103) nicht über den Antrieb miteinander verbunden sind und relativ zueinander manuell schwenkbar sind,
dadurch gekennzeichnet, dass
der erste und der zweite Teil (3;103) ferner Anschläge (16a,16b,9;127, 128) aufweisen, die nur in der zweiten Position der Kupplung (12; 111) in einer entgegengesetzten Schwenkrichtung zusammenwirken, um die vorbestimmte Position zu definieren, wobei die Anschläge (16a,16b,9; 127,128) in der ersten Position der Kupplung (12;111) nicht aktiv sind und nur in der zweiten Position der Kupplung (12;111) aktiv sind.

2. Gelenkaktuator nach Anspruch 1, bei dem der erste Teil (2;102) eine Basisplatte (4;104) mit einer Basiswelle (5;105) aufweist und bei der der zweite Teil (3;103) einen Halterahmen (3) aufweist, der um die Basiswelle (5;105) herum verläuft, um ein Spiegelgehäuse zu halten.

3. Gelenkaktuator nach Anspruch 2, bei dem die Kupplung (12;111) einen Kupplungsring aufweist, der relativ zu der Basiswelle (5;105) lösbar drehgekoppelt ist und axial zwischen der ersten und der zweiten Position bewegbar ist.

4. Gelenkaktuator nach einem der vorhergehenden Ansprüche, bei dem die in der entgegengesetzten Schwenkrichtung zusammenwirkenden Anschläge (16a,16b,9;127,128), derart angeordnet sind, dass die auftretenden Reaktionskräfte in der gleichen Größenordnung liegen wie die Reaktionskräfte, die beim Zusammenwirken der Anschläge in der Schwenkrichtung auftreten.

5. Gelenkaktuator nach einem der vorhergehenden Ansprüche, bei dem der Aktuator einen Abschaltmechanismus zum Abschalten des Antriebs aufweist und bei dem die zum Überwinden der in der entgegengesetzten Schwenkrichtung zusammenwirkenden Anschläge (16a,16b,9;127, 128) erforderliche Kraft mindestens in der gleichen Größenordnung liegt wie die Kraft, mit der der Antrieb von dem Abschaltmechanismus abgeschaltet wird.

6. Gelenkaktuator nach Anspruch 5, bei dem der Abschaltmechanismus eine Strombegrenzungsschaltung aufweist und bei dem der zum Überwinden der in der entgegengesetzten Schwenkrichtung zusammenwirkenden Anschläge (16a,16b) benötigte elektrische Strom in dem elektrischen Antrieb mindestens in der gleichen Größenordnung liegt wie der Strom, bei dem die Strombegrenzungsschaltung den Antrieb abschaltet.

7. Gelenkaktuator nach einem der Ansprüche 2-6, bei dem die zusammenwirkenden Anschläge von mindestens einem Nocken (9;109), der an dem Halterahmen angeordnet ist, um beim Schwenken des Halterahmens einen Weg zu durchlaufen, und von mindestens einem ersten Anschlag (8a,8b;108a), der relativ zu der Basiswelle fest positioniert ist, gebildet sind und bei dem die in entgegengesetzter Schwenkrichtung zusammenwirkenden Anschläge (16a,16b,9;127,128) von dem Nocken (16a,16b;127), der an dem Halterahmen angeordnet ist, und mindestens einem zweiten Anschlag (9;128), der derart angeordnet ist, dass er relativ zu der Basiswelle axial bewegbar ist, gebildet sind.

8. Gelenkaktuator nach einem der Ansprüche 3-7, bei dem der Kupplungsring als Zahnrad (12;112) ausgebildet ist, das mit einem Ausgangsteil des elektrischen Antriebs in Zusammengriff steht und das in der ersten Position relativ zu der Basiswelle (5;105) drehfest arretiert ist und in der zweiten Position relativ zu der Basiswelle frei drehbar ist.

9. Gelenkaktuator nach einem der Ansprüche 3-8, bei dem zwischen dem Kupplungsring und dem Spiegelhalterahmen ein Hilfs-Kupplungsring (13;126) um die Basiswelle herum angeordnet ist.

10. Gelenkaktuator nach Anspruch 9, bei dem der Hilfs-Kupplungsring (13; 126) und der Spiegelhalterahmen Hilfsanschläge (16a,16b;128) aufweisen, die in der zweiten Position der Kupplung (12;111) in der entgegengesetzten Schwenkrichtung zusammenwirken und die die Anschläge zum Definieren der vorbestimmten Position in der entgegengesetzten Schwenkrichtung bilden.

11. Gelenkaktuator nach einem der vorhergehenden Ansprüche, ferner mit einem Zwischenring (129), der um die Basiswelle (105) herum angeordnet ist, auf den eine axiale Federkraft wirkt und der in der ersten Position der Kupplung (111) an dem Spiegelhalterahmen gehalten ist und der in der zweiten Position an dem Kupplungsring (126) gehalten ist.

12. Gelenkaktuator nach einem der Ansprüche 3-11, bei dem die Basiswelle (105) an ihrem Umfang eine Anzahl von mit zwei oberen Teilen versehene Profile (122) aufweist und bei dem der Kupplungsring (126) Nocken aufweist, die jeweils mit den mit zwei oberen Teilen versehenen Profilen zusammenwirken.

13. Gelenkaktuator nach Anspruch 12, bei dem der Kupplungsring in einer ersten Position der Kupplung in einer ersten Axialposition in Axialrichtung an der Basiswelle (105) gehalten ist und über Nocken, die in den Tälern zwischen den mit zwei oberen Teilen versehenen Profilen aufgenommen sind, drehfest arretiert ist.

14. Gelenkaktuator nach einem der Ansprüche 3-13, bei dem der Kupplungsring (126) in der ersten Position der Kupplung (111) von einer ersten Axialposition in eine zweiten Axialposition axial bewegbar ist.

15. Gelenkaktuator nach einem der vorhergehenden Ansprüche 9-14, bei dem der Kupplungsring in der zweiten Position der Kupplung (12;111) an dem Hilfs-Kupplungsring (13;126) gehalten ist.

16. Gelenkaktuator nach Anspruch 15, bei dem der Kupplungsring in der zweiten Position der Kupplung in einer zweiten Axialposition in Richtung der ersten Position mit einer axialen Federkraft beaufschlagt ist und über die nach unten weisenden Nocken an dem Hilfs-Kupplungsring (13;126) gehalten ist.

17. Gelenkaktuator nach einem der vorhergehenden Ansprüche, bei dem der Hilfs-Kupplungsring (13;126) in der zweiten Position an dem Halterahmen gehalten ist.

18. Gelenkaktuator nach Anspruch 7, bei dem der Weg in der ersten Position des Kupplungsrings von einer ersten Nockenbahn gebildet ist, die an einem Basisring vorgesehen ist, welcher relativ zu der Basiswelle (5; 105) fest montiert ist, und bei dem der Weg in der zweiten Position des Kupplungsrings teilweise von einer zweiten Nockenbahn gebildet ist, die an dem Hilfsring vorgesehen ist, welcher drehfest arretiert ist und relativ zu dem Basisring axial bewegbar ist.

19. Gelenkaktuator nach Anspruch 18, bei dem der Hilfsring (13;126) an dem Kupplungsring anliegt.

Revendications

1. Actionneur articulé (1, 101) comprenant une première partie (2 ; 102) qui est raccordée avec une seconde partie (3 ; 103) via un entraînement électrique, dans lequel la première et la seconde partie (3 ; 103) sont dotées de butées (8a, 8b, 9 ; 108a, 109a) coopérant dans une direction de pivotement pour définir une position prédéterminée des parties d'actionneur l'une par rapport à l'autre, dans lequel en outre un couplage (12 ; 111) est prévu entre la première et la seconde partie, de sorte que dans une première position du couplage (12 ; 111) la première partie (2 ; 102) et la seconde partie (3 ; 103) sont raccordées via l'entraînement et peuvent être pivotées l'une par rapport à l'autre avec l'entraînement, et dans une seconde position, la première partie (2 ; 102) et la seconde partie (3 ; 103) ne sont pas raccordées via l'entraînement et peuvent être pivotées l'une par rapport à l'autre manuellement, caractérisé en ce que la première et la seconde partie (3 ; 103) sont en outre dotées de butées (16a, 16b, 9 ; 127, 128) coopérant uniquement dans la seconde position du couplage (12 ; 111) dans une direction de pivotement opposée, pour définir la position prédéterminée, lesquelles butées (16a, 16b, 9 ; 127, 128) ne sont pas actives dans la première position du couplage (12 ; 111) et ne sont actives que dans la seconde position du couplage (12 ; 111).

2. Actionneur articulé selon la revendication 1, dans lequel la première partie (2 ; 102) comprend une plaque de base (4 ; 104), dotée d'un arbre de base (5 ; 105), et dans lequel la seconde partie (3 ; 103) comprend un châssis de support (3) s'étendant autour de l'arbre de base (5 ; 105) pour supporter un boîtier de miroir.

3. Actionneur articulé selon la revendication 2, dans lequel le couplage (12 ; 111) comprend une bague de couplage qui, par rapport à l'arbre de base (5 ; 105) est couplée en rotation de manière dégageable et axialement mobile entre la première et la seconde position.

4. Actionneur articulé selon l'une quelconque des revendications précédentes, dans lequel les butées (16a, 16b, 9 ; 127, 128) coopérant dans la direction de pivotement opposée, sont agencées de sorte que les forces de réaction occurrentes sont du même ordre de grandeur que les forces de réaction se produisant suite à la coopération des butées dans la direction de pivotement.

5. Actionneur articulé selon l'une quelconque des revendications précédentes, dans lequel l'actionneur est doté d'un mécanisme d'arrêt pour arrêter l'entraînement, et dans lequel la force nécessaire pour maîtriser les butées (16a, 16b, 9 ; 127, 128) coopérant dans la direction de pivotement opposée est au moins du même ordre de grandeur que la force à laquelle l'entraînement est arrêté par le mécanisme d'arrêt.

6. Actionneur articulé selon la revendication 5, dans lequel le mécanisme d'arrêt comprend un circuit de limitation de courant, et dans lequel le courant électrique dans l'entraînement électrique nécessaire pour maîtriser les butées (16a, 16b) coopérant dans la direction de pivotement opposée, est au moins du même ordre de grandeur que le courant auquel le circuit de limitation de courant arrête l'entraînement.

7. Actionneur articulé selon l'une quelconque des revendications 2 à 6, dans lequel les butées coopérantes sont formées par au moins une came (9 ; 109) qui est agencée sur le châssis de support pour traverser un passage pendant le pivotement du châssis de support et au moins une première butée (8a, 8b ; 108a), positionnée de manière fixe par rapport à l'arbre de base, et dans lequel les butées (16a, 16b, 9 ; 127, 128) coopérant dans une direction de pivotement opposée sont formées par la came (16a, 16b ; 127) qui est agencée sur le châssis de support et au moins une seconde butée (9 ; 128) qui est agencée afin d'être axialement mobile par rapport à l'arbre de base.

8. Actionneur articulé selon l'une quelconque des revendications 3 à 7, dans lequel la bague de couplage est conçue comme une roue dentée (12 ; 112) qui est en mise en prise avec une partie de sortie de l'entraînement électrique et qui, dans la première position, est bloquée contre la rotation par rapport à l'arbre de base (5 ; 105) et dans la seconde position peut tourner librement par rapport à l'arbre de base.

9. Actionneur articulé selon l'une quelconque des revendications 3 à 8, dans lequel entre l'anneau de couplage et le châssis de support de miroir, une bague de couplage auxiliaire (13 ; 126) est incluse autour de l'arbre de base.

10. Actionneur articulé selon la revendication 9, dans lequel la bague de couplage auxiliaire (13 ; 126) et le châssis de support de miroir sont dotés de butées auxiliaires (16a, 16b ; 128) coopérant dans la seconde position du couplage (12 ; 111) dans la direction de pivotement opposée, qui constituent les butées pour définir la position prédéterminée dans la direction de pivotement opposée.

11. Actionneur articulé selon l'une quelconque des revendications précédentes, comprenant en outre une bague intermédiaire (129) agencée autour de l'arbre de base (105), qui est sous l'action de rappel axial et qui, dans la première position du couplage (111), est supportée sur un châssis de support de miroir et qui, dans la seconde position, est supportée sur la bague de couplage (126).

12. Actionneur articulé selon l'une quelconque des revendications 3 à 11, dans lequel l'arbre de base (105) au niveau de sa circonférence, est doté d'un certain nombre de profils à deux sommets (122), et dans lequel la bague de couplage (126) est dotée de cames, chacune pour la coopération avec les profils à deux sommets.

13. Actionneur articulé selon la revendication 12, dans lequel la bague de couplage, dans une première position du couplage, dans une première position axiale, est supportée dans la direction axiale sur l'arbre de base (105) et est bloquée contre la rotation via des cames qui sont reçues dans des creux entre les profils à deux sommets.

14. Actionneur articulé selon l'une quelconque des revendications 3 à 13, dans lequel la bague de couplage (126) dans la première position du couplage (111) est axialement mobile d'une première position axiale à une seconde position axiale.

15. Actionneur articulé selon l'une quelconque des revendications précédentes 9 à 14, dans lequel la bague de couplage dans la seconde position du couplage (12 ; 111) est supportée sur la bague de couplage auxiliaire (13 ; 126).

16. Actionneur articulé selon la revendication 15, dans lequel la bague de couplage, dans la seconde position du couplage, dans une seconde position axiale, est sous l'action de rappel axial dans la direction de la première position et est supportée sur la bague de couplage auxiliaire (13 ; 113) via des cames descendantes.

17. Actionneur articulé selon l'une quelconque des revendications précédentes, dans lequel la bague de couplage auxiliaire (13 ; 113) dans la seconde position est supportée sur le châssis de support.

18. Actionneur articulé selon la revendication 7, dans lequel le passage dans la première position de la bague de couplage est formé par un premier chemin de came qui est prévu sur une bague de base qui est montée de manière fixe par rapport à l'arbre de base (5 ; 105) et dans lequel le passage dans la seconde position de la bague de couplage est partiellement formé par un second chemin de came qui est prévu sur une bague auxiliaire qui est bloquée contre la rotation et axialement mobile par rapport à la bague de base.

19. Actionneur articulé selon la revendication 18, dans lequel la bague auxiliaire (13 ; 126) vient en butée contre la bague de couplage.

Drawing